US4680982A - Circulating-ball drive - Google Patents

Circulating-ball drive Download PDF

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Publication number
US4680982A
US4680982A US06/474,228 US47422883A US4680982A US 4680982 A US4680982 A US 4680982A US 47422883 A US47422883 A US 47422883A US 4680982 A US4680982 A US 4680982A
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Prior art keywords
nut
spindle
turns
ball
groove
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Expired - Fee Related
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US06/474,228
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Richard Wilke
Helmut Korthaus
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
    • F16H25/2209—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls with arrangements for taking up backlash
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L59/00—Thermal insulation in general
    • F16L59/12—Arrangements for supporting insulation from the wall or body insulated, e.g. by means of spacers between pipe and heat-insulating material; Arrangements specially adapted for supporting insulated bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
    • F16H2025/2242—Thread profile of the screw or nut showing a pointed "gothic" arch in cross-section
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/19698—Spiral
    • Y10T74/19702—Screw and nut
    • Y10T74/19721—Thread geometry
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/19698—Spiral
    • Y10T74/19702—Screw and nut
    • Y10T74/19744—Rolling element engaging thread
    • Y10T74/19749—Recirculating rolling elements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/1987—Rotary bodies
    • Y10T74/19893—Sectional
    • Y10T74/19898—Backlash take-up
    • Y10T74/19902—Screw and nut

Definitions

  • Our present invention relates to a circulating-ball drive in which a spindle or leadscrew and an associated nut coact with interposed bearing balls which are guided in an outer helical groove of the spindle and an inner helical groove of the nut.
  • the turns of the latter groove form part or one or more closed tracks for the recirculation of these balls, e.g. as described in our prior U.S. Pat. Nos. 3,942,846 and 4,080,011.
  • the object of our present invention is to provide an improved circulating-ball drive which does not require individual machining of different turns of a helical groove, enables the use of identical bearing balls in the entire assembly and substantially equalizes the stress destribution among these balls over a wide range of loads.
  • our invention is applicable to an assembly of the type referred to in which the spindle or leadscrew, whose outer helical groove has a multiplicity of turns of uniform cross-section, is virtually nondeformable in both the axial and the radial direction while the associated nut, whose inner helical groove has a lesser number of turns also of uniform cross-section, is only axially deformable within certain limits of elasticity.
  • Each turn of each groove has a profile of two symmetrical flanks engaging a set of bearing balls--confined between that turn and a confronting turn of the opposite groove--along a helical contact line whereby each confined ball is in two-point contact with the spindle and with the nut, as known per se.
  • the turns of the outer groove have a pitch which exceeds by a small fraction the pitch of the turns of the inner groove in an unstressed state of the assembly
  • the difference in pitch should be very small, generally on the order of one hundredth of 1%.
  • FIG. 1 is an axial sectional view of half a circulating-ball drive embodying our invention, shown in an unloaded position;
  • FIGS. 2 and 3 are views similar to FIG. 1, showing the assembly under axial pressure from opposite sides.
  • the assembly shown in the drawing comprises a nut 11 with a helical inner groove 13 of several turns confronting respective turns of an outer groove 14 of an associated leadscrew or spindle 12.
  • the two grooves 13 and 14 are of constant, mutually symmetrical profiles with pointed arches of the "Gothic" type, e.g. as known per se from FIG. 1.2 of the above-identified German publication.
  • the symmetrical flanks of each groove profile define a pair of helical contact lines bracketing a multiplicity of identical bearing balls 15 between them. Under no-load conditions, as illustrated in FIG.
  • each ball 15 is therefore in contact with nut 11 and spindle 12 at four points lying at the corners of a rectangle, namely points A1 and A2 of groove 13 and points B1 and B2 of groove 14.
  • Nut 11 is further provided with one or more nonillustrated return passages for the recirculation of the balls, as is well known in the art.
  • the turns of helical groove 13 prior to assembly have a pitch h N which is very slightly less than the pitch h S of the turns of groove 14.
  • the balls 15 are gripped uniformly at contact points A1, A2 and B1, B2 so as to be subjected to a certain compression in the direction of spindle axis Z; the balls so confined, accordingly, offer a certain but not significant resistance to relative rotation of the nut and the spindle.
  • FIG. 2 it has been assumed that a substantial axial force P L acts upon the nut 11, e.g. as a result of a rotation of spindle 12 in a sensetending to shift that nut to the left along with a nonillustrated load entrained thereby.
  • the axial thrust thus exerted upon nut 11 causes a minute shift of the turns of its groove 13 to the right, relative to the confronting turns of spindle groove 14, whereby pressure upon the balls 15 is intensified at contact points A1 and B2 but is essentially relieved at the other contact points A2 and B1 shown in FIG. 1, tending toward zero under maximum load.
  • An opposite thrust, exerted by a relative pressure P R has been illustrated in FIG.
  • the two-point strong contact and two-point relieved contact existing in the loaded positions of FIGS. 2 and 3 reduces the rolling resistance of the balls 15 so as to enable an easier relative rotation of the spindle and the nut.
  • This differential is of the order of magnitude of the usual machining tolerances, ranging between about 0 and 4 ⁇ , which are absorbed by the elastic deformability of the balls and their guide tracks.
  • the pitch differential ⁇ h is cumulative so as to amount to 8 ⁇ over the distance indicated in FIGS. 2 and 3.
  • the elastic axial deformation of nut 11 due to the pitch differential results in a virtually uniform distribution of force P L or P R upon the balls 15 occupying the several turns of nut groove 13.
  • the described nut structure therefore, is bilaterally effective in a manner comparable to that of conventional double nuts of the "O" or "X" type (with contact pressures exerted upon the balls in directions diverging or converging toward the axis), e.g. as shown in FIG. 2.5 of the above-identified German publication, while being considerably more compact and easier to machine.
  • the illustrated Gothic groove profiles may be modified as long as each groove has two flanks making only symmetrical point contact with the confined balls under no-load conditions.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

A spindle or leadscrew and an associated nut, forming part of a driving assembly of the circulating-ball type, have helical threads of symmetrical profiles in the shape of pointed arches whose flanks engage the recirculating balls along respective helical contact lines. With the spindle virtually non-deformable in the axial direction, the pitch of its thread exceeds that of the nut thread (in the absence of stress upon the latter) by a small differential--specifically 0.02%--lying well within the limits of elastic axial deformability of the nut. Upon rotation of the spindle relative to the nut for the transmission of an axial force, this differential results in an approximately uniform stress distribution among the sets of balls lying in confronting turns of the spindle and nut threads.

Description

FIELD OF THE INVENTION
Our present invention relates to a circulating-ball drive in which a spindle or leadscrew and an associated nut coact with interposed bearing balls which are guided in an outer helical groove of the spindle and an inner helical groove of the nut. The turns of the latter groove form part or one or more closed tracks for the recirculation of these balls, e.g. as described in our prior U.S. Pat. Nos. 3,942,846 and 4,080,011.
BACKGROUND OF THE INVENTION
Such circulating-ball drives have become increasingly popular in recent years, thanks to their low-friction coupling of the relatively rotatable members. It is commonly accepted that the load should be distributed as uniformly as possible among all the balls, that these balls should have substantially identical diameters and that the grooves of the spindle and the nut should be of constant cross-section throughout their lengths while being of the same pitch in both members. This has been pointed out in a comprehensive study by H. Hilmer, titled Rechnergestutzte Auslegung und Berechnung von Kugelgewindespindeln, appearing in Vol. 11 of the German series called Fertigungstechnische Berichte edited by Prof. Hans Kurt Tonshoff, published 1978 by Technischer Verlag Resch KG in the German Federal Republic.
As particularly discussed on page 79 of that publication, section 5.3.1., the stress exerted upon the balls in the several turns of the nut groove is not uniform under the aforestated conditions. According to the study, as specifically noted in sections 5.4-5.5 on pages 94-100 of that publication, a uniformization of the stress could be achieved by varying the outer diameter and thus the cross-sectional area of the nut, by modifying the flanks of the groove profile from one turn to the next in order to change the relative bending resistance of the intervening ribs, or by using balls of different diameters in the several turns (which of course calls for a separate recirculation passage for each turn). The author has found, however, that these proposed solutions are fully effective only for a limited load range; the corresponding discussion appears on pages 99-100 of the cited publication.
OBJECT OF THE INVENTION
The object of our present invention, therefore, is to provide an improved circulating-ball drive which does not require individual machining of different turns of a helical groove, enables the use of identical bearing balls in the entire assembly and substantially equalizes the stress destribution among these balls over a wide range of loads.
SUMMARY OF THE INVENTION
Our invention is applicable to an assembly of the type referred to in which the spindle or leadscrew, whose outer helical groove has a multiplicity of turns of uniform cross-section, is virtually nondeformable in both the axial and the radial direction while the associated nut, whose inner helical groove has a lesser number of turns also of uniform cross-section, is only axially deformable within certain limits of elasticity. Each turn of each groove has a profile of two symmetrical flanks engaging a set of bearing balls--confined between that turn and a confronting turn of the opposite groove--along a helical contact line whereby each confined ball is in two-point contact with the spindle and with the nut, as known per se. According to our present improvement, the turns of the outer groove have a pitch which exceeds by a small fraction the pitch of the turns of the inner groove in an unstressed state of the assembly
The difference in pitch should be very small, generally on the order of one hundredth of 1%.
BRIEF DESCRIPTION OF THE DRAWING
The above and other features of our invention will now be described in detail with reference to the accompanying drawing in which:
FIG. 1 is an axial sectional view of half a circulating-ball drive embodying our invention, shown in an unloaded position; and
FIGS. 2 and 3 are views similar to FIG. 1, showing the assembly under axial pressure from opposite sides.
SPECIFIC DESCRIPTION
The assembly shown in the drawing, generally designated 10, comprises a nut 11 with a helical inner groove 13 of several turns confronting respective turns of an outer groove 14 of an associated leadscrew or spindle 12. The two grooves 13 and 14 are of constant, mutually symmetrical profiles with pointed arches of the "Gothic" type, e.g. as known per se from FIG. 1.2 of the above-identified German publication. The symmetrical flanks of each groove profile define a pair of helical contact lines bracketing a multiplicity of identical bearing balls 15 between them. Under no-load conditions, as illustrated in FIG. 1, each ball 15 is therefore in contact with nut 11 and spindle 12 at four points lying at the corners of a rectangle, namely points A1 and A2 of groove 13 and points B1 and B2 of groove 14. Nut 11 is further provided with one or more nonillustrated return passages for the recirculation of the balls, as is well known in the art.
In accordance with our present invention, the turns of helical groove 13 prior to assembly have a pitch hN which is very slightly less than the pitch hS of the turns of groove 14. The pitch difference Δh=hS -hN is so small as to be unnoticeable in FIG. 1 in which the assembly is unloaded as indicated by zero axial forces PL and PR acting upon the nut 11 from the left and from the right. Under these circumstances the balls 15 are gripped uniformly at contact points A1, A2 and B1, B2 so as to be subjected to a certain compression in the direction of spindle axis Z; the balls so confined, accordingly, offer a certain but not significant resistance to relative rotation of the nut and the spindle. It is assumed that spindle 12 is virtually nondeformable in both axial and radial directions and that nut 11 is also radially nondeformable for practical purposes; to this end it may be desirable to encase the nut in a rigidifying shell as disclosed in our prior U.S. Pat. No. 4,080,011 referred to above. The pitch difference Δh is such that nut 11 will be axially stretched, under all operating conditions, within the limits of its elastic deformability as given by the range of proportionality of Hooke's law.
In FIG. 2 it has been assumed that a substantial axial force PL acts upon the nut 11, e.g. as a result of a rotation of spindle 12 in a sensetending to shift that nut to the left along with a nonillustrated load entrained thereby. The axial thrust thus exerted upon nut 11 causes a minute shift of the turns of its groove 13 to the right, relative to the confronting turns of spindle groove 14, whereby pressure upon the balls 15 is intensified at contact points A1 and B2 but is essentially relieved at the other contact points A2 and B1 shown in FIG. 1, tending toward zero under maximum load. An opposite thrust, exerted by a relative pressure PR, has been illustrated in FIG. 3 which shows the balls 15 in strong contact with nut 11 only at points A2 and with spindle 12 only at points B1, the points A1 and B2 remaining contact points with relieved force as described. The cumulative pitch difference between four turns of groove 13 in the unstressed state of nut 11 and as many turns of groove 14 will be 4hS - 4hN =4Δh as diagrammatically and exaggeratedly indicated in FIGS. 2 and 3.
The two-point strong contact and two-point relieved contact existing in the loaded positions of FIGS. 2 and 3 reduces the rolling resistance of the balls 15 so as to enable an easier relative rotation of the spindle and the nut.
In a specific example, pitch hX =10 mm and pitch hn =9.998 mm which corresponds to a differential Δh=2μ or 0.02%. This differential is of the order of magnitude of the usual machining tolerances, ranging between about 0 and 4μ, which are absorbed by the elastic deformability of the balls and their guide tracks. Whereas, however, the deviations from a true helical path due to these tolerances will generally cancel one another in the several turns, the pitch differential Δh is cumulative so as to amount to 8μ over the distance indicated in FIGS. 2 and 3.
As will be readily apparent from the foregoing description, the elastic axial deformation of nut 11 due to the pitch differential results in a virtually uniform distribution of force PL or PR upon the balls 15 occupying the several turns of nut groove 13. The described nut structure, therefore, is bilaterally effective in a manner comparable to that of conventional double nuts of the "O" or "X" type (with contact pressures exerted upon the balls in directions diverging or converging toward the axis), e.g. as shown in FIG. 2.5 of the above-identified German publication, while being considerably more compact and easier to machine.
The illustrated Gothic groove profiles may be modified as long as each groove has two flanks making only symmetrical point contact with the confined balls under no-load conditions.

Claims (4)

We claim:
1. A circulating-ball drive comprising a spindle, a unitary one-piece nut coaxially surrounding said spindle along part of the length thereof, and a set of identical bearing balls interposed between said spindle and said nut, said spindle having a single outer helical groove of uniform cross-section with a multiplicity of turns, said nut having a single inner helical groove of uniform cross-section with a plurality of turns confronting respective turns of said outer groove and forming part of at least one closed track for the recirculation of bearing balls confined between the confronting turns, each of said turns having a profile with two symmetrical flanks engaging the confined bearing balls along a helical contact line whereby each confined ball is exclusively in two-point continuous contact with each of said spindle and said nut over the full length of a path for each ball in contact with both said spindle and said nut, the turns of said outer groove having a constant pitch over the length thereof exceeding by a small fraction the pitch of the turns of said inner groove which is constant over the length thereof in an unstressed state of said nut over the full length of said nut, with resulting uniform elastic axial deformation of said nut upon assembly so that under all operating conditions said grooves engage each ball with four-point contact exclusively during the travel of each ball over the length of said spindle.
2. A circulating-ball drive as defined in claim 1 wherein the pitch of said outer groove exceeds the pitch of said inner groove by a differential on the order of one-hundredth of one percent.
3. A circulating-ball drive as defined in claim 1 wherein said confronting turns have mutually symmetrical profiles.
4. A circulating-ball drive as defined in claim 3 wherein said profiles are in the shape of pointed arches.
US06/474,228 1982-03-12 1983-03-11 Circulating-ball drive Expired - Fee Related US4680982A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3209086 1982-03-12
DE3209086A DE3209086C1 (en) 1982-03-12 1982-03-12 Ball screw drive

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DD (1) DD207562A5 (en)
DE (1) DE3209086C1 (en)
ES (1) ES278027Y (en)
FR (1) FR2523248B1 (en)
GB (1) GB2117082B (en)
HU (1) HU188244B (en)
IN (1) IN158191B (en)
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US5239882A (en) * 1991-05-16 1993-08-31 Transrol Screw-nut device of rolling bearing type with adjustable clearance or preload
US5245884A (en) * 1989-09-05 1993-09-21 British Aerospace Public Limited Company Ball screw mechanism
DE4412539A1 (en) * 1993-04-12 1994-10-13 Nsk Ltd Ball screw
US5535638A (en) * 1994-11-10 1996-07-16 Cincinnati Milacron Inc. Antifriction screw drive
US5809838A (en) * 1995-05-30 1998-09-22 Nsk Ltd. Ball screw device with means for maintaining balance
US5946974A (en) * 1997-03-27 1999-09-07 Kabushiki Kaisha Toshiba Ball screw mechanism
US6010420A (en) * 1995-08-21 2000-01-04 Ntn Corporation Pulley, ball bearing and fan for preventing the occurence of abnormal noise under cold ambient conditions
US6584869B2 (en) * 2000-07-21 2003-07-01 Mannesmann Sachs Ag Ball screw
US20040107788A1 (en) * 2002-09-16 2004-06-10 Fred Kramer Axial adjusting device with multiple ball means
US20040182190A1 (en) * 2003-03-17 2004-09-23 Tetsuya Murakami Electric power steering apparatus
US6813969B2 (en) 2002-07-01 2004-11-09 Delphi Technologies, Inc. Rocker return liner for ball nut
US20050235766A1 (en) * 2001-08-03 2005-10-27 Nsk Ltd. Ball screw
US20070000342A1 (en) * 2005-06-16 2007-01-04 Keisuke Kazuno Ball screw
US20070137350A1 (en) * 2003-09-11 2007-06-21 Ntn Corporation Ball screw nut and method of producing the same
US20070240532A1 (en) * 2004-05-26 2007-10-18 Schaeffler Kg Spindle Nut for a Ball Screw
US7587954B2 (en) * 2003-05-30 2009-09-15 Ina-Schaeffler Kg Ball screw
US20130008275A1 (en) * 2010-03-31 2013-01-10 Nsk Ltd. Method for Manufacturing Nut for Ball Screw and Ball Screw
US20130152716A1 (en) * 2011-12-16 2013-06-20 Aktiebolaget Skf Roller screw
US20160061303A1 (en) * 2014-06-09 2016-03-03 Hiwin Technologies Corp. Offset preload ball screw with expandable loading area

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JP2009138944A (en) * 2009-02-06 2009-06-25 Nsk Ltd Ball screw device
DE102020122920A1 (en) * 2020-09-02 2022-03-03 Schaeffler Technologies AG & Co. KG Switchable rocker arm for a valve drive of an internal combustion engine

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FR2414141A1 (en) * 1978-01-04 1979-08-03 Luc Jacques Worm and wheel speed reduction gear - has steel balls running in track tubes and grooves between teeth to reduce friction
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Title
"Rechnergestutzte Auslegung Und Berechnung Von Kugelgewindespindeln" by H. Hilmer, published in vol. II of Fertigungstechnische Berichte, 1978.
Rechnergest tzte Auslegung Und Berechnung Von Kugelgewindespindeln by H. Hilmer, published in vol. II of Fertigungstechnische Berichte, 1978. *

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US5245884A (en) * 1989-09-05 1993-09-21 British Aerospace Public Limited Company Ball screw mechanism
JPH06147289A (en) * 1991-05-16 1994-05-27 Transrol Screw body and nut device
US5239882A (en) * 1991-05-16 1993-08-31 Transrol Screw-nut device of rolling bearing type with adjustable clearance or preload
JP3299302B2 (en) 1991-05-16 2002-07-08 トランスロール Screw and nut device
DE4412539C2 (en) * 1993-04-12 2002-06-27 Nsk Ltd Ball screw
DE4412539A1 (en) * 1993-04-12 1994-10-13 Nsk Ltd Ball screw
US5749265A (en) * 1993-04-12 1998-05-12 Nsk, Ltd. Ball screw device
US5535638A (en) * 1994-11-10 1996-07-16 Cincinnati Milacron Inc. Antifriction screw drive
US5809838A (en) * 1995-05-30 1998-09-22 Nsk Ltd. Ball screw device with means for maintaining balance
US6227994B1 (en) 1995-08-21 2001-05-08 Ntn Corporation Pulley, ball bearing and belt transmitting device
US6010420A (en) * 1995-08-21 2000-01-04 Ntn Corporation Pulley, ball bearing and fan for preventing the occurence of abnormal noise under cold ambient conditions
US5946974A (en) * 1997-03-27 1999-09-07 Kabushiki Kaisha Toshiba Ball screw mechanism
US6584869B2 (en) * 2000-07-21 2003-07-01 Mannesmann Sachs Ag Ball screw
US7201076B2 (en) * 2001-08-03 2007-04-10 Nsk Ltd. Ball screw
US20050235766A1 (en) * 2001-08-03 2005-10-27 Nsk Ltd. Ball screw
US20050061098A1 (en) * 2002-07-01 2005-03-24 Delphi Technologies, Inc. Rocker return liner for ball nut
US6813969B2 (en) 2002-07-01 2004-11-09 Delphi Technologies, Inc. Rocker return liner for ball nut
US20040107788A1 (en) * 2002-09-16 2004-06-10 Fred Kramer Axial adjusting device with multiple ball means
US7252017B2 (en) * 2002-09-16 2007-08-07 Gkn Viscodrive Gmbh Axial adjusting device with multiple ball means
US20040182190A1 (en) * 2003-03-17 2004-09-23 Tetsuya Murakami Electric power steering apparatus
US7281604B2 (en) * 2003-03-17 2007-10-16 Koyo Seiko Co., Ltd. Electric power steering apparatus
US7587954B2 (en) * 2003-05-30 2009-09-15 Ina-Schaeffler Kg Ball screw
US20070137350A1 (en) * 2003-09-11 2007-06-21 Ntn Corporation Ball screw nut and method of producing the same
US20110035930A1 (en) * 2004-05-26 2011-02-17 Schaeffler Technologies Gmbh & Co. Kg Spindle nut for a ball screw
US8800129B2 (en) 2004-05-26 2014-08-12 Schaeffler Technologies Gmbh & Co. Kg Method for producing a spindle nut for a ball screw
US20070240532A1 (en) * 2004-05-26 2007-10-18 Schaeffler Kg Spindle Nut for a Ball Screw
US7536928B2 (en) * 2005-06-16 2009-05-26 Ntn Corporation Ball screw
US20070000342A1 (en) * 2005-06-16 2007-01-04 Keisuke Kazuno Ball screw
US20130008275A1 (en) * 2010-03-31 2013-01-10 Nsk Ltd. Method for Manufacturing Nut for Ball Screw and Ball Screw
US8950283B2 (en) * 2010-03-31 2015-02-10 Nsk Ltd. Method for manufacturing nut for ball screw and ball screw
US20130152716A1 (en) * 2011-12-16 2013-06-20 Aktiebolaget Skf Roller screw
US9267588B2 (en) * 2011-12-16 2016-02-23 Aktiebolaget Skf Roller screw
US20160061303A1 (en) * 2014-06-09 2016-03-03 Hiwin Technologies Corp. Offset preload ball screw with expandable loading area

Also Published As

Publication number Publication date
SE8300279L (en) 1983-09-13
IN158191B (en) 1986-09-20
ES278027Y (en) 1985-05-16
IT1171660B (en) 1987-06-10
JPS58166160A (en) 1983-10-01
FR2523248B1 (en) 1989-03-17
GB2117082B (en) 1985-10-09
IT8320031A0 (en) 1983-03-11
GB8305251D0 (en) 1983-03-30
GB2117082A (en) 1983-10-05
SE449249B (en) 1987-04-13
DE3209086C1 (en) 1983-04-07
HU188244B (en) 1986-03-28
ES278027U (en) 1984-11-16
SE8300279D0 (en) 1983-01-20
DD207562A5 (en) 1984-03-07
FR2523248A1 (en) 1983-09-16

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